EP0505349A2 - Vérin hydraulique - Google Patents

Vérin hydraulique Download PDF

Info

Publication number
EP0505349A2
EP0505349A2 EP92890058A EP92890058A EP0505349A2 EP 0505349 A2 EP0505349 A2 EP 0505349A2 EP 92890058 A EP92890058 A EP 92890058A EP 92890058 A EP92890058 A EP 92890058A EP 0505349 A2 EP0505349 A2 EP 0505349A2
Authority
EP
European Patent Office
Prior art keywords
piston
pressure
cylinder
arrangement according
limiting member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP92890058A
Other languages
German (de)
English (en)
Other versions
EP0505349A3 (en
EP0505349B1 (fr
EP0505349B2 (fr
Inventor
Gerhard Dipl.-Ing. Huber (Fh)
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hoerbiger GmbH
Original Assignee
Hoerbiger Fluidtechnik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=3495386&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0505349(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Hoerbiger Fluidtechnik GmbH filed Critical Hoerbiger Fluidtechnik GmbH
Publication of EP0505349A2 publication Critical patent/EP0505349A2/fr
Publication of EP0505349A3 publication Critical patent/EP0505349A3/de
Publication of EP0505349B1 publication Critical patent/EP0505349B1/fr
Application granted granted Critical
Publication of EP0505349B2 publication Critical patent/EP0505349B2/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices

Definitions

  • the invention relates to a hydraulic cylinder / piston arrangement, with a cylinder which has at least on one side of a piston adjustable therein a work space connected to the outside via a connecting line for hydraulic medium and furthermore a locking device for locking the piston in the event of failure of the hydraulic medium pressure.
  • Hydraulically operated working cylinders are used today in a wide variety of contexts for the movement or adjustment of device and machine parts or the like.
  • the essential advantages are the simplicity and operational reliability of these components and the fact that any sub-translation or translation of speed and lifting power can be achieved within wide limits.
  • Arrangements of the type mentioned are known for example from AT-PS 302.107, DE-OS 27 27 506, DE-OS 31 43 040, or also DE-OS 37 32 561 and are mostly used for safety reasons where the piston or the components moved by this should be determined or locked in the event of a sudden failure of the pressure of the working medium to avoid uncontrolled movements.
  • locking elements act mechanically on the piston or a piston rod connected to it, the actuation of these locking elements usually also taking place via the or a pressure medium; apart from this, an electrical actuation would also be conceivable and possible.
  • the object of the present invention is to improve an arrangement of the type mentioned at the outset in such a way that the disadvantages of the known arrangements of this type are avoided and that, in particular, a simple structure of the locking device is made possible which, in addition, requires at least a temporary manual actuation of the without special repair work otherwise allowed over the piston adjusted component.
  • the locking device has a pressure-limiting member in at least one connection line, which is open when the piston is hydraulically adjusted and is closed when there are no pressurized connections, and from a certain pressurization thereof in the associated one Hydraulic medium located in the work area opens due to a force applied via the piston. If and as long as the piston is hydraulically adjusted in the intended manner, the function of the cylinder / piston arrangement according to the invention is essentially unchanged compared to the known cylinder / piston arrangements. When the piston is at a standstill or the connections are depressurized, no more hydraulic medium is conveyed via the connecting line to or from the work space and the pressure limiting element is closed.
  • the invention thus relates to a locking device acting purely hydraulically on the piston, the basic function of which can also be implemented via a closed position provided on the control valves of such cylinder / piston arrangements.
  • the main difference is that a control valve is only accidentally in the closed position in the event of a sudden loss of pressure in the working medium, and in the other two positions there is an immediate loss of pressure in the entire system, which makes a controlled determination of the piston impossible, while at the arrangement according to the invention in the event of a failure of the connection pressure at the same time as the piston is at a standstill, the closing of the pressure limiting member and thus the fixing of the piston take place.
  • an opening device which, when the piston is actuated hydraulically, keeps the pressure limiting member open or bypasses it. This can ensure that the working pressure required for the normal operation of the cylinder / piston arrangement is not for the actuation of the pressure limiting member to open it needs to be increased.
  • an embodiment of the invention is particularly advantageous, according to which the opening device has a cylinder / piston adjusting arrangement which is hydraulically connected to the respective opposite working space in the cylinder and whose piston holds a spring-loaded valve element in the connecting line of the working space assigned to the pressure limiting member when pressure is applied.
  • Appropriate cross-sectional dimensions of this adjustment arrangement can be used to ensure in a simple manner that the pressure-limiting element is opened at the normal working pressure of the overall arrangement.
  • the hydraulic medium pressure acting to adjust the working piston in the direction of a reduction in the working space assigned to the pressure-limiting element in the opposite working space thus also serves to keep the valve element open, which, bypassing the pressure-limiting element, enables largely unimpeded flow of the hydraulic medium out of the reducing working space, so that the normal hydraulic actuation of the working piston is not significantly hindered and no separate pressure connections or the like are required for this actuation of the valve element.
  • the pressure-limiting element can have a closing element that seals the connecting line on a fixed sealing surface and is spring-loaded. Via the choice or setting of the spring load of this closing element, the pressurization, from which the pressure limiting element opens to overcome the determination of the working piston, can be predetermined or varied in cooperation with the size of the contact surface for the pressure to be limited.
  • the closing element can have a central connecting bore for the connecting line, which interacts with the valve element and one with the piston Cylinder / piston adjustment assembly associated actuating pin with play.
  • the closing element of the pressure-limiting member and the valve element cooperate essentially concentrically to facilitate the normal adjustment of the working piston, which enables a simple and compact structure of the arrangement.
  • the hydraulic medium can flow in and out via the play between the actuating pin and the central connecting bore.
  • a further embodiment of the invention is advantageous, according to which a throttle point is provided in the connecting line. This acts as a so-called outlet throttle, which prevents the working piston from jerking in by keeping a low back pressure in the piston chamber.
  • the pressure limiting member, opening device, valve element and throttle point are arranged in a bore in the housing of the cylinder, which is closed to the outside and connects the hydraulic connection of the cylinder to the working space.
  • the hydraulic cylinder / piston arrangement shown consists essentially of a housing 1 which receives a cylinder 2 which has 3 working spaces 4, 5 on each side of a piston 2 adjustable in this cylinder 2, each of which has connection lines 6, 7 for hydraulic medium are externally connected to hydraulic connections 8.
  • the piston 3, which is sealed by a seal 10 in the cylinder 2 is connected to a piston rod 9, which projects out of the housing 1 at the upper end thereof in the illustration and is used for actuating device or machine parts (not shown).
  • a receiving part 11 is provided with a connection bore 12, by means of which the entire arrangement can be fixed, for example, to a machine bed or the like, or also rotatably.
  • An insert 13 is provided as the upper limit of the upper working chamber 5 in the illustration, which ensures seals against the piston rod 9 on the one hand and the receiving bore 16 in the housing 1 on the other hand via seals 14, 15 and centers the piston rod 9 on a guide sleeve 17.
  • This insert part 13 is held in the receiving bore 16 via a retaining ring 18 arranged in a groove 19.
  • a mechanical end position damping for the illustrated upper setting of the piston 3 is provided, which consists of disks 20, 21 and 22 with damping elements 23 in between.
  • stepped bore 24 of the housing 1 which is closed to the outside via a cover 26 held with a retaining ring 25 and which connects the lower hydraulic connection 8 of the cylinder 2 to the working chamber 4 in the illustration, is a pressure limiting device 27, a valve element 28, a throttle point 29 and an opening device 30 for the valve element 28 are arranged.
  • the closing ball 31 of the valve element 28 is inserted together with a load body 33, which is pushed upward via a spring 32 in the illustration, from the upper side in the illustration into a stepped bore 34 in the cover 26. From the lower side, the throttling point 29 is inserted into a likewise graduated further bore 35, which in turn is connected with a screw 37 sealed by a seal 36 is completed.
  • the pressure limiting member 27 has a closing element 41, which seals via a spring 38 against a sealing surface formed on a sealing ring 39 at the upper end of the bore 34 in the cover 26 in the illustration, which has a central connecting bore 42 for the connecting line 7 going from the working space 4 to the hydraulic connection 8 Has.
  • This connecting bore 42 cooperates at its lower end in the illustration with the closing ball 31 of the valve element 28 and is thereby closed when the arrangement is depressurized.
  • the closing element 41 is provided laterally perpendicular to the connecting bore 42 with a bore 43 which is substantially aligned with the bore 44 in the housing 1 leading to the hydraulic connection 8.
  • the opening device 30 is arranged, which has a cylinder / piston adjusting arrangement 45 hydraulically connected to the opposite working chamber 5, the piston 46 of which, when pressure is applied via the connecting line 47, the valve element 28 or its closing ball 31 via an actuating pin 48 keeps open.
  • the arrangement shown makes it possible to determine the piston rod 9 or the piston 3 in any position against a defined counterforce F L. This is done in the following way:
  • the counterforce F L acts in the direction of the force.
  • a pressure which corresponds to the load F L arises in the piston-side working chamber 5, the hydraulic medium in this working chamber 5 being closed off.
  • the closing ball 31 of the valve element 28 seals at the lower end of the connecting bore 42 in the illustration, and the closing element 41 of the pressure-limiting member 27 is pressed onto the sealing ring 39 by the prestressing of the spring 38 and also seals there.
  • the closing element 41 opens on the sealing surface 40 and allows hydraulic medium to flow out of the working space 4 to the associated hydraulic connection 8.
  • the hydraulic medium takes the path through the lateral bore 49 at the lower end of the working space 4 in the illustration, the connecting bores 50 in the cover 26, the throttle point 29, the outer diameter of the loading body 33, the outer diameter of the closing ball 31, the opened sealing surface 40 the area of the bore 24 receiving the spring 38 and the bore 44 for the hydraulic connection 8.
  • the cylinder / piston arrangement is now to be retracted hydraulically, the corresponding pressure is applied to the upper hydraulic connection 8 in the illustration.
  • This acts on the one hand in the working space 5 from above on the piston 3 and on the other hand via the connecting line 47 on the piston 46 of the cylinder / piston adjusting arrangement 45 or the opening device 30.
  • the piston 46 thus moves downward in the illustration and presses it the closing ball 31 from its seat at the lower end of the connecting bore 42 down.
  • the diameter ratio between the piston 46 and the sealing point of the closing ball 31 is so large that even a low pressure is sufficient to lift the closing ball 31 against a pressure (load pressure) prevailing in the working space 4.
  • the hydraulic medium located in the working space 4 can now flow off to the hydraulic connection 8 with only a slight pressure drop via the play between the actuating pin 48 and the connecting bore 42 and via the bore 43.
  • the throttle point 29 is provided as a so-called discharge throttle, which prevents the piston 3 from jerkily retracting by maintaining a low counterpressure in the working space 4.
  • the annular disk 51 on the upper side of the piston 46 in the illustration has only the function of a spacer disk.
  • the screw plug 37 allows a simple replacement of the throttle point 29 so that the suitable nozzle diameter can be selected for the respective load case. With an optimized nozzle diameter the locking screw 37 could of course also be omitted and the cover 26 could not be drilled out at this point.
  • the throttling effect could also be achieved by a corresponding design of the bores 50, which could then open directly into the installation space for the spring 32.
  • the piston 3 can be extended differentially or simply.
  • the hydraulic medium flows from the lower hydraulic connection 8 through the bore 43 and the play between the connecting bore 42 and the actuating pin 48, opens the closing ball 31 against the only slightly preloaded spring 32 and flows further through the throttle point 29, the bores 50 and the bore 49 in the Working space 4, with which the piston 3 extends together with the piston rod 9.
  • the pressure in the working space 5 supports the opening of the closing ball 31 in the manner already described above.
  • the mechanical damping already mentioned above in the upper region of the arrangement shown acts in that, shortly before the start of damping, the disks 20, 21, 22 are at a certain distance and the damping rings 23 are each round. If the piston 3 now moves onto the disks when extending, the deformation of the damping elements 23 brakes the end stop.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
EP92890058A 1991-03-20 1992-03-17 Vérin hydraulique Expired - Lifetime EP0505349B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0061991A AT402334B (de) 1991-03-20 1991-03-20 Hydraulische zylinder/kolben-anordnung
AT619/91 1991-03-20

Publications (4)

Publication Number Publication Date
EP0505349A2 true EP0505349A2 (fr) 1992-09-23
EP0505349A3 EP0505349A3 (en) 1993-03-03
EP0505349B1 EP0505349B1 (fr) 1995-05-24
EP0505349B2 EP0505349B2 (fr) 1998-05-27

Family

ID=3495386

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92890058A Expired - Lifetime EP0505349B2 (fr) 1991-03-20 1992-03-17 Vérin hydraulique

Country Status (4)

Country Link
US (1) US5235896A (fr)
EP (1) EP0505349B2 (fr)
AT (1) AT402334B (fr)
DE (1) DE59202285D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1084883A2 (fr) * 1999-09-13 2001-03-21 Wilhelm Karmann GmbH Véhicule convertible

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5490443A (en) * 1988-04-13 1996-02-13 Atsuta; Yuzuru Pressure-discharged type retaining system
US5402866A (en) * 1993-01-08 1995-04-04 International Transouip Industries, Inc. Brake assembly with new locking mechanism
US5400694A (en) * 1994-03-04 1995-03-28 Mcneilus Truck And Manufacturing, Inc. Hydraulic cylinder with internal safety valve
DE10142884A1 (de) 2001-09-03 2003-03-27 Stabilus Gmbh Auslöseeinrichtung für ein blockierbares Kolben-Zylinderaggregat
US8444128B2 (en) * 2008-09-04 2013-05-21 Vektek, Inc. Double acting work support with internal sequence control
US11241780B2 (en) * 2017-12-07 2022-02-08 Maxell Izumi Co., Ltd. Electric tool
JP7320924B2 (ja) * 2018-05-22 2023-08-04 ナブテスコ株式会社 流体圧バルブ

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1197483A (en) * 1966-10-21 1970-07-08 Caterpillar Tractor Co Overridable Check Valve Mechanism
US3943968A (en) * 1975-01-06 1976-03-16 Parker-Hannifin Corporation Combination lock and relief valve for hydraulic systems
EP0051728A1 (fr) * 1980-11-08 1982-05-19 Robert Bosch Gmbh Dispositif de commande pour un vérin hydraulique
EP0163771A2 (fr) * 1984-05-10 1985-12-11 KLB Hydrosystem GmbH Soupape de verrouillage pour frein de descente
US4667570A (en) * 1984-12-21 1987-05-26 The Boeing Company Integral hydraulic blocking and relief valve

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2633871A (en) * 1949-08-02 1953-04-07 John B Parsons Electromagnetic control valve device for fluid pressure systems or the like
GB734434A (en) * 1953-01-24 1955-08-03 Carbodies Ltd Means for operating a drop-head of a motor-car body
US3274902A (en) * 1965-10-22 1966-09-27 Deere & Co Hydraulic control system
US3747351A (en) * 1971-10-22 1973-07-24 Bertea Corp Hydraulic system
US3908515A (en) * 1973-09-10 1975-09-30 Caterpillar Tractor Co Hydraulic circuit with selectively actuatable float control
US3933167A (en) * 1974-02-20 1976-01-20 Tomco, Inc. Pilot operated check valve
FR2427499A1 (fr) * 1978-06-01 1979-12-28 Sarrazin Applic Hydr Dispositif de commande integre pour circuit de fluide, et ses applications
SU724805A1 (ru) * 1978-09-01 1980-03-30 Проектно-Конструкторский И Технологический Институт Кузробот Односторонний гидравлический замок гидроцилиндра
US4244275A (en) * 1979-01-15 1981-01-13 Abex Corporation Counterbalance valve
DE2946765C2 (de) * 1979-11-20 1986-04-30 Thyssen Industrie Ag, 4300 Essen Entsperrbares Rückschlagventil
SU885644A1 (ru) * 1979-12-13 1981-11-30 Предприятие П/Я В-8664 Гидросистема управлени
SU879065A1 (ru) * 1980-01-14 1981-11-07 Тульский Проектно-Конструкторский Технологический Институт Комбайностроения "Проектин" Гидропривод
GB2073564B (en) * 1980-04-15 1983-06-08 Thomas K H Plough turn-over mechanism
JPS5765403A (en) * 1980-10-07 1982-04-21 Mitsuwa Seiki Co Ltd Lifter for cab
JPS57107405A (en) * 1980-12-24 1982-07-03 O G Giken Kk Hydraulic operating device
US4429529A (en) * 1981-11-20 1984-02-07 Applied Power Inc. Hydraulic control system having reciprocating pump and handle operated rotating valve
US5081904A (en) * 1989-08-30 1992-01-21 Aladdin Engineering & Mfg., Inc. Locking valve and flow control valve assembly

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1197483A (en) * 1966-10-21 1970-07-08 Caterpillar Tractor Co Overridable Check Valve Mechanism
US3943968A (en) * 1975-01-06 1976-03-16 Parker-Hannifin Corporation Combination lock and relief valve for hydraulic systems
EP0051728A1 (fr) * 1980-11-08 1982-05-19 Robert Bosch Gmbh Dispositif de commande pour un vérin hydraulique
EP0163771A2 (fr) * 1984-05-10 1985-12-11 KLB Hydrosystem GmbH Soupape de verrouillage pour frein de descente
US4667570A (en) * 1984-12-21 1987-05-26 The Boeing Company Integral hydraulic blocking and relief valve

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1084883A2 (fr) * 1999-09-13 2001-03-21 Wilhelm Karmann GmbH Véhicule convertible
EP1084883A3 (fr) * 1999-09-13 2002-11-20 Wilhelm Karmann GmbH Véhicule convertible

Also Published As

Publication number Publication date
AT402334B (de) 1997-04-25
EP0505349A3 (en) 1993-03-03
ATA61991A (de) 1996-08-15
EP0505349B1 (fr) 1995-05-24
US5235896A (en) 1993-08-17
DE59202285D1 (de) 1995-06-29
EP0505349B2 (fr) 1998-05-27

Similar Documents

Publication Publication Date Title
DE69208435T2 (de) Druckflüssigkeitszylinder mit Druckübersetzer
DE3318550A1 (de) Hubvorrichtung, insbesondere hebebuehne fuer kraftfahrzeuge
DE3620753A1 (de) Hydraulischer kraftschrauber
EP0279315B1 (fr) Dispositif de commande hydraulique
EP1101692B1 (fr) Dispositif de commande hydraulique
EP0505349B1 (fr) Vérin hydraulique
DE1630752B2 (de) Druckmittelgespeistes Federelement für Fahrzeuge mit innerer Niveauregeleinrichtung zum Anschluß an eine außenliegende Druckmittelquelle, insbesondere hydropneumatisches Federbein
DE2513013A1 (de) Hydraulisches wegeventil zur steuerung des druckmittelflusses zu und von einem doppelseitig beaufschlagbaren hydraulikzylinder
EP0975856B1 (fr) Soupape avec dispositif de commande hydraulique
DE1282886B (de) Hydropneumatisches Hubaggregat
DE102005052116B4 (de) Einrichtung zur Sicherung der Bewegungsreihenfolge von mindestens zwei fluidbetätigten Verdrängereinheiten
DE2407296C2 (de) Bremskraftverstärker
DE4414779C1 (de) Multifunktionsventil
DE2915505C2 (fr)
DE1219817B (de) Bremskraftregler fuer Fahrzeuge, insbesondere Kraftfahrzeuge
EP0967028B1 (fr) Presse hydraulique
EP0163771A2 (fr) Soupape de verrouillage pour frein de descente
DE2554594A1 (de) Steuerventil fuer hydraulisch betaetigte kippfahrzeuge
DE2549394C3 (de) Einrichtung zur Anzeige der Endstellungen des Arbeitskolbens eines doppeltwirkenden druckmittelbetatigten Stellmotors
DE2725948A1 (de) Pneumatisches bremsventil fuer fahrzeuge
DE2519973C3 (de) Entlastungsventil
DE19641540C2 (de) Hydraulisches Sicherheitsventil
DE1243980B (de) Hydraulische Hubeinrichtung mit hydraulischem Kolbenrueckzug
DE2821550C2 (de) Bremsventil zum Steuern des Hydraulikfluiddrucks in Fahrzeugbremsen
DE2450330B2 (de) Doppelhydraulischer stellantrieb

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE FR IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR IT

17P Request for examination filed

Effective date: 19930708

17Q First examination report despatched

Effective date: 19941013

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR IT

REF Corresponds to:

Ref document number: 59202285

Country of ref document: DE

Date of ref document: 19950629

ITF It: translation for a ep patent filed

Owner name: ING. C. GREGORJ S.P.A.

ET Fr: translation filed
PLAV Examination of admissibility of opposition

Free format text: ORIGINAL CODE: EPIDOS OPEX

PLBQ Unpublished change to opponent data

Free format text: ORIGINAL CODE: EPIDOS OPPO

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

PLAV Examination of admissibility of opposition

Free format text: ORIGINAL CODE: EPIDOS OPEX

PLBF Reply of patent proprietor to notice(s) of opposition

Free format text: ORIGINAL CODE: EPIDOS OBSO

26 Opposition filed

Opponent name: APPLIED POWER INCORPORATED

Effective date: 19960221

PLBF Reply of patent proprietor to notice(s) of opposition

Free format text: ORIGINAL CODE: EPIDOS OBSO

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: HOERBIGER GMBH

PLAW Interlocutory decision in opposition

Free format text: ORIGINAL CODE: EPIDOS IDOP

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19980220

Year of fee payment: 7

PLAW Interlocutory decision in opposition

Free format text: ORIGINAL CODE: EPIDOS IDOP

PUAH Patent maintained in amended form

Free format text: ORIGINAL CODE: 0009272

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: PATENT MAINTAINED AS AMENDED

27A Patent maintained in amended form

Effective date: 19980527

AK Designated contracting states

Kind code of ref document: B2

Designated state(s): DE FR IT

ITF It: translation for a ep patent filed

Owner name: ING. C. GREGORJ S.P.A.

ET3 Fr: translation filed ** decision concerning opposition
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19990225

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19991130

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20010103

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050317